JP7186507B2 - Server cooling system and server cooling method - Google Patents

Description

TECHNICAL FIELD The present invention relates to a server cooling system and a server cooling method for cooling servers mounted in a rack or the like in a row.

For example, conventionally, in a data center or the like, a plurality of various servers are mounted in a rack called a server rack and housed in a room. In order to ensure proper operation, conventionally, these server devices (including electronic devices such as information technology, measurement systems, and communication systems; hereinafter sometimes referred to as "server devices") are provided with cooling fans. . The cooling fan sucks in, for example, supply air that is lower than room temperature supplied from an air conditioner, cooling coil, etc., to cool the server, and the heated air after cooling is exhausted from the server equipment.

Using the external static pressure of the cooling fan built into the server equipment, the cooling fan sucks in the air supplied from the cooling coil installed in the upper part of the rack and circulates the heated air to the cooling coil. As a server cooling system, there is one disclosed in Patent Document 1. More specifically, in the technique described in Patent Document 1, a plurality of server devices mounted on a rack are all arranged in parallel, and air supplied to the front side of each server device is distributed to each server device. are sucked in in parallel, and the air that has risen in temperature after cooling is exhausted in parallel on the back side of each server device, and the exhaust air from each server device is collected, ventilated to the cooling coil, and uniformly I was trying to form a nice airflow.

JP 2017-117475 A

By the way, there are several types of servers, and a host machine that houses a computing device installed with a server operating system and a storage cabinet that houses storage devices such as hard disks are mounted in one rack. There is

The host machine has a built-in central processing unit with high heat integration density, and it is common to provide a space around the central processing unit so that the heat generated from the central processing unit can be diffused. is. Therefore, ventilation resistance for cooling is less than that of a storage cabinet, which will be described later. Therefore, an axial cooling fan is mainly used because it can obtain a large air volume relative to the static pressure.

On the other hand, since the storage cabinet contains a plurality of rectangular parallelepiped hard disks in close proximity, the ventilation resistance for cooling is greater than that of the aforementioned host machine. Therefore, a centrifugal cooling fan is mainly used because it can obtain a high static pressure relative to the air volume.

A centrifugal fan can obtain a pressure increase by the square of the ratio of the suction port diameter and the discharge port diameter of the impeller due to centrifugal force. has the characteristic that it is easier to obtain a higher pressure than the axial flow type.

Figure 1 shows the relationship between the external static pressure of the server equipment and the air volume. Airflow and external static pressure were measured at different resistances and plotted on a graph. Furthermore, from the characteristics of each single host machine and storage cabinet, a state in which one host machine and six storage cabinets were operated in parallel was calculated and plotted. In the graph, assuming the resistance in the cooling coil and the air passage between the server and the upper heat exchanger formed in the system in Patent Document 1, the pressure loss at each air volume is shown as a resistance curve.

As can be seen from this graph, when 1 host machine and 6 storage cabinets are operated in parallel, the operating point at a1 moves to a2 in stand-alone operation, making it difficult to obtain a high pressure axial flow system. A host machine that uses a cooling fan from the Decrease in airflow results in insufficient cooling capacity, which makes it impossible to properly remove the heat generated inside the equipment, causing the temperature inside the equipment to rise, leading to malfunctions and deterioration of durability of the equipment. If it exceeds, the protective device may stop the operation of the equipment. In the graph, b1 is the operating point for single storage cabinet operation, b2 is the operating point for the storage cabinet during parallel operation, and c is the operating point for one host machine and six storage cabinets.

The present invention has been made in view of this point. It is an object of the present invention to appropriately cool each server device by appropriately forming an airflow blowing from the server device in consideration of the characteristics of a cooling fan having a cooling fan.

In order to achieve the above object, the present invention provides a first server device having a first fan as a cooling fan and a second server device having a second fan having an air volume characteristic smaller than that of the first fan as a cooling fan. a rack provided, a heat exchange device disposed on the top or side of the rack and used for cooling the first server device and the second server device, and the suction side of the first server device and the second server device and a second space formed on the blow-out side of the first server device and the second server device, the server cooling system used in the first server device The first fan has a characteristic of easily obtaining an air volume larger than that of the second fan employed in the second server device, and the second fan used in the second server device is the first server device. It has a characteristic that it is easy to obtain a higher static pressure than the first fan that is employed, has a flow path that guides the air blown out from the second server device to the suction side of the first server device, and It is characterized by having a shielding plate that blocks the air blown out from the first server device from flowing to the blowing side of the second server device .

According to the invention, said first space constitutes a cold aisle, said second space constitutes a hot aisle, and cold air from said heat exchanger is introduced into said first space. The second fan of the second server device has a characteristic of easily obtaining an air volume larger than that of the first fan of the first server device, and the air blown out from the second server device is sucked into the first server device. Since there is a flow path leading to the side, it is possible to ensure an appropriate amount of airflow for the first server device and the second server device, and it is possible to realize suitable cooling for each.

The second space may have a shielding plate that separates the blowout side area of the first server device from the blowout side area of the second server device.

A gap for passing the air blown from the second server device may be airtightly secured in the upper portion, the lower portion, or the side portion of the second server device.

A convection prevention plate having a depth equal to or greater than the height of the void and a width equal to or greater than the width of the second server device may be provided above the void in the first space.

The position of the suction surface of the first server device may be configured to be offset from the edge of the convection prevention plate by a distance equal to or greater than the height of the gap.

The width of the first space may be equal to or narrower than the widths of the first server device and the second server device.

A blowout auxiliary fan may be provided on the second space side for assisting the blowout of air from the second server device.

A suction auxiliary fan may be provided on the first space side for assisting the suction of the first server device.

For example, the first fan may be a centrifugal fan, and the second fan may be, for example, an axial fan.

According to still another aspect of the present invention, a first server device having a first fan as a cooling fan and a second server device having a second fan having an air volume characteristic smaller than that of the first fan as a cooling fan are provided. heat exchange equipment arranged on the top or side of the rack and used for cooling the first server equipment and the second server equipment; and on the suction side of the first server equipment and the second server equipment a first space formed on the blow-out side of the first server device and the second server device; A server cooling method comprising a shielding plate for blocking the flow of air into the server, wherein the first fan used in the first server equipment is the second fan used in the second server equipment The second fan used in the second server device has a characteristic of easily obtaining a larger air volume, and the second fan used in the second server device has a characteristic of easily obtaining a higher static pressure than the first fan used in the first server device. and guiding the air blown out from the second server device to the suction side of the first server device.

According to the present invention, the characteristics of the different cooling fans used in the server equipment are taken into account to appropriately form the airflow of the air blown out from the server equipment. It can be carried out.

4 is a graph showing air volume vs. external static pressure characteristics showing operating points of the host machine and the storage cabinet; It is an explanatory view showing an outline of composition of a cooling system concerning an embodiment of the invention. 1 is a perspective view of a cooling system according to an embodiment of the invention; FIG. FIG. 2 is an explanatory diagram schematically showing the configuration of a cooling system having a shield plate on the hot aisle side; FIG. 2 is an explanatory view schematically showing the configuration of a cooling system having a shield plate on the hot aisle side and a convection suppression plate on the cold aisle side; FIG. 2 is an explanatory diagram schematically showing the configuration of a cooling system having an exhaust auxiliary fan; FIG. 4 is an explanatory view schematically showing the configuration of a cooling system having an exhaust auxiliary fan on the hot aisle side shielding plate and a suction auxiliary fan on the cold aisle side shielding plate.

FIG. 2 shows an outline of the configuration of the cooling system 1 according to the embodiment, and this figure mainly shows the flow of low-temperature supply air SA, exhaust EA, and return air RA. is omitted.

In this example, the host machine 11 as the second server device is at the bottom, and six storage cabinets 21 to 26 as the first server device are arranged vertically above it. In this example, the host machine 11 is provided with an axial fan as a cooling fan, and the storage cabinets 21 to 26 are provided with centrifugal fans as cooling fans. A heat exchange unit 2 such as a cooling coil is installed on the uppermost storage cabinet 26 .

The suction surfaces 11a, 21a-26a of the host machine 11 and the storage cabinets 21-26 are directed, for example, toward the front side (the right side in FIG. 2), and the host machine 11 and the exhaust surfaces of the storage cabinets 21-26 are exhausted. The surfaces 11b, 21b to 26b are oriented, for example, toward the rear side (left side in FIG. 2).

Spaces in the outer casing (not shown) on the side of the suction surfaces 11a and 21a to 26a of the host machine 11 and the storage cabinets 21 to 26 form a cold aisle CL as a first space. The spaces on the side of the exhaust surfaces 11b, 21b to 26b of the storage cabinets 21 to 26 form a hot aisle HL as a second space.

In this cooling system 1, the exhaust EAH from the exhaust surface 11b of the lowermost host machine 11 does not flow to the hot aisle HL, but passes through the gap between the host machine 11 and the storage cabinet 21, for example, to the cold aisle CL. It is designed to flow to the side. That is, in this example, instead of installing the host machine 11 and the storage cabinets 21 to 26 in parallel, only the host machine 11 is installed upstream of the storage cabinets 21 to 26, and arranged in series in terms of airflow. ing.

With this configuration, the operating point of the cooling fan of the host machine 11 shifts to the a1 side of the graph in FIG. 1, and the host machine 11 can obtain a predetermined air volume. As a result, each server device, ie, the host machine 11 and the storage cabinets 21 to 26 can be cooled appropriately. As a result of confirmation by simulation, it was predicted that the airflow direction of the cooling fan of the host machine would be reversed in the conventional technology, whereas the airflow direction would be normal in the above example.

As described above, according to the embodiment, in consideration of the air volume characteristics of the cooling fans provided in the host machine 11 and the storage cabinets 21 to 26, the warm air blown from the host machine 11 to the hot aisle HL is cooled to the cold aisle. Since the air is led to the CL, the host machine 11 can also be cooled by taking in an appropriate amount of air. That is, the cooling fan provided in the host machine 11 has smaller airflow characteristics and a lower external static pressure than the cooling fans provided in the storage cabinets 21 to 26, so that the air blown from the host machine 11 is kept in a cold aisle. This is because the cold air on the cold aisle CL side can be sucked from the suction surface 11a of the host machine 11 by guiding the cold air to the CL side.

Therefore, the air volume characteristic as used in the present invention means a capacity characteristic indicating the magnitude of the influence of the external static pressure. Therefore, a small air volume characteristic means that a large air volume can be obtained easily, but the air volume is easily affected by the external static pressure. From a different point of view, the cooling fan provided in the host machine 11 has a characteristic and structure that makes it easier to obtain a larger air volume than the cooling fans provided in the storage cabinets 21-26. The provided cooling fan has a characteristic and structure that makes it easier to obtain a higher static pressure than the cooling fan provided in the host machine 11 .

Next, another embodiment will be described. FIG. 3 shows a perspective view of a cooling system 1 for explaining cooling systems according to various embodiments described below.

In this cooling system 1, a host machine 11 and storage cabinets 21 to 26 are mounted on a server rack 3 in order from the bottom. This server rack 3 complies with, for example, Japanese Industrial Standard JIS C6010-2:1998 "Modular order of racks and unit chassis for electronic equipment" level 4 "housing".

If the host machine 11 is installed at a height other than the lowest, the depth of the host machine 11 is generally longer than the depth of the storage cabinets 21-26. If it protrudes, the flow path for the exhaust gas to return to the heat exchanging part 2 as return air becomes narrow, resulting in an increase in air resistance. As a result, the cooling air volume is reduced, and the cooling capacity is reduced. Therefore, it is preferable to install the host machine 11 at the bottom.

The outside of the server rack 3 is surrounded by an outer casing 5 made of an airtight panel material covering the entire six sides of the server rack 3 and the upper heat exchange section 2 . In this example, a base 12 is installed on the underside of the host machine 11 . A space D is formed between the upper surface of the host machine 11 and the lower surface of the storage cabinet 21 .

Sealing materials 31 and 32 are provided on both sides of the host machine 11 and the storage cabinets 21 to 26, respectively, between the cold aisle CL on the front side (front side) and the hot aisle HL on the back side of these server devices. airtightness is enhanced. In the cooling system 1 having such a basic configuration, the addition or configuration of the following members can be singly or plurally combined.

[Shield]
Between the hot aisle HL side of the host machine 11 and the hot aisle HL side of the storage cabinet 21, a shielding plate 41 extending in the horizontal direction is provided to divide and partition the area of the hot aisle HL in an airtight manner up and down. good too. That is, the shielding plate 41 is installed so as to separate and shield the blowout side area of the storage cabinet 21 and the blowout side area of the host machine 11 in the hot aisle HL. Therefore, the blowing-side area is an area where warm air blown from the storage cabinet 21 and the host machine 11 is blown. Warm air blown out from a normal server device of this type is blown out in a horizontal direction. becomes a region (space) corresponding to .

By providing the shielding plate 41 as described above, together with the airtightness of the sealing materials 31 and 32, the warm air accompanying the exhaust EAH from the host machine 11 can be prevented from causing airtightness between the host machine 11 and the storage cabinet 21. It is possible to suitably flow to the cold aisle CL side through the gap D having the properties. On the other hand, it is also possible to prevent warm air blown from the storage cabinet 21 to the hot aisle HL from flowing into the hot aisle HL of the host machine 11 . As a result, the formation of the airflow shown in FIG. 4 can be properly formed, and the host machine 11 can take in a sufficient amount of air supply, and the storage cabinets 21 to 26 can also be cooled appropriately. be able to.

[Gap]
The air gap D described above serves as a flow path for the exhaust EAH from the host machine 11 to flow into the cold aisle CL. has the effect of reducing the recirculation of the exhaust EAH to the suction surface 11a of the host machine 11 by ventilating only from above the host machine 11. FIG.

The size of the gap D, that is, the height of the gap D, preferably secures a height exceeding 0.5 times the height h of the host machine 11 . If the height of the air gap D is insufficient, the pressure loss in the flow path increases, and there is a risk that a sufficient amount of cooling air for the host machine 11 cannot be obtained. Therefore, the lower limit of the height of the air gap D is appropriately 0.5 times the height h of the host machine 11. Assuming an aperture ratio of 50%, the air intake opening of the suction surface 11a of the host machine 11 is It is desirable that the gap D has a cross-sectional area equal to or greater than the effective area.

[Convection suppression plate]
As shown again in FIG. 3, above the air gap D on the side of the cold aisle CL, a convection prevention plate having a depth equal to or greater than the height of the air gap D and a width equal to or greater than the width of the storage cabinet 21 is provided. 51 may be provided. The convection suppression plate 51 does not block the suction side area corresponding to the suction surfaces 21a and 11a of the storage cabinet 21 and the host machine 11, that is, the area corresponding to the suction surfaces 21a and 11a in the cold aisle CL. It is a partition.

By providing the convection prevention plate 51 having such a configuration, the exhaust EAH flowing into the cold aisle CL side from the gap D is caused to flow upward from both sides of the convection prevention plate 51 by natural convection as shown in FIG. to rectify the airflow. By doing so, the convection caused by the air density difference between the warm air from the exhaust EAH flowing in from the gap D and the cold air SA from the heat exchange section 2 is guided to both sides of the storage cabinet 21, and is maximized. It can be lifted up to the upper storage cabinet 26 . In addition, the cold air from the heat exchange unit 2 and the warm air are mixed in the process of rising, and the mixed air is gradually diffused, so that the warm air from the exhaust EAH discharged from the host machine 11 is transferred to the storage cabinets 21 to 26. can be distributed evenly.

In addition, it is possible to prevent the warm air from the exhaust EAH flowing from the gap D from being drawn into the suction surface 21a of the storage cabinet 21 located directly above the host machine 11 and the gap D. As a result, the cooling of the host machine 11 and the storage cabinet 21 located directly above the gap D can be prevented from being hindered.

A punching plate or the like may be used as the convection prevention plate 51, and instead of the convection prevention plate 51, a distribution duct for distributing the warm air from the gap D may be installed in the cold aisle CL.

[Baffle plate for air vent]
As shown in FIG. 3, a vent baffle 6 having an opening 6a is provided above the cold aisle CL at a position serving as an inlet for introducing cold air from the heat exchange section 2 into the cold aisle CL. may In this case, cold air from the heat exchange section 2 descends through the opening 6a. On the other hand, when the convection prevention plate 51 is installed, warm air blown from the exhaust surface of the host machine 11 flows upward from both sides of the convection prevention plate 51 due to natural convection. Therefore, the cold air from the heat exchange section 2 is prevented from interfering with the above-described warm air on the way. As a result, the cold air from the heat exchanging section 2 can be preferably guided to the suction surface 11a side of the host machine 11 . Of course, the cold air from the heat exchange section 2 can also be efficiently sent to the suction surfaces 21a-26a of the storage cabinets 21-26. From this point of view, the vent baffle 6 having the opening 6a has the effect of substantially narrowing the width of the cold aisle CL, as will be described later.

The width and position of the opening 6a of the vent baffle plate 6 may be set corresponding to the convection suppression plate 51 , for example, in view of such action. That is, the width of the opening 6a is set to be the same as the width of the convection suppression plate 51, and the position of the opening 6a itself is set so as to be positioned between the front end of the convection suppression plate 51 and the outer casing 5. good too. That is, it may be set so that the convection suppression plate 51 does not cover the inside of the opening 6a when viewed from above. Of course, even if a part of the convection suppressing plate 51 covers the inside of the opening 6a when viewed from above, the essential effect of suppressing the midway interference between the cool air and the warm air is not greatly reduced. The width of the opening 6a is set equal to the substantial width of the suction surfaces 21a to 26a of the storage cabinets 21 to 26 and the suction surface 11a of the host machine 11a (the width of the area where cold air is actually sucked). You may

[Host Machine Offset Allocation]
As described above, when the convection prevention plate 51 is installed, the position of the suction surface 11a of the host machine 11 is offset from the end of the convection prevention plate 51 by a distance equal to or greater than the height of the air gap D. is preferred. The offset here means that the suction surface 11a of the host machine 11 protrudes from the suction surface 21a of the storage cabinet 21 toward the cold aisle CL, as shown in FIG.

If the position of the suction surface 11a of the host machine 11 is at the same position as the storage cabinet 21 or at the edge of the convection suppression plate 51, the rate at which the warm air flowing in from the gap D is drawn into the suction surface 11a of the host machine 11 increases. Therefore, the cooling effect in the host machine 11 may be impaired. Therefore, the position of the suction surface 11a of the host machine 11 is offset from the end of the convection suppression plate 51 by a distance equal to or greater than the height of the gap D, so that the warm air flowing in from the gap D is The rate at which the suction surface 11a of the host machine 11 sucks can be reduced. As a result, deterioration of the cooling effect in the host machine 11 can be suppressed.

[Width of cold aisle]
The width of the cold aisle CL may be set equal to or narrower than the width of each of the host machine 11 and the storage cabinets 21-26. In the cooling system 1, for example, as shown in FIGS. 4 and 5, cold air from the heat exchange section 2 falls to the storage cabinets 21 to 26 and the cold aisle CL of the host machine 11. FIG. In such a case, if the width of the cold aisle CL is not restricted, the airflow rising from both sides of the convection suppression plate 51 due to natural convection interferes with the cold air descending from the heat exchange section 2, and is discharged from the host machine 11. There is a possibility that the warm air cannot be evenly distributed to the storage cabinets 21 to 26 and the host machine 11 . Since the kinetic energy of the cold air from the heat exchange part 2 is greater than that of the rising warm air, the convection is pushed back at the lower position, and the lower server equipment such as the storage cabinets 21 and 22 and the host machine 11 The temperature of the intake air of the

In order to suppress this, the width of the cold aisle CL, which is the cold air flow path, may be made equal to or narrower than the width of the storage cabinets 21 to 26 and the host machine 11 . For example, by narrowing the cold aisle CL directly above the portion where the warm air from both sides of the convection prevention plate 51 rises, the airflow rising from both sides of the convection prevention plate 51 and the cold air from the heat exchange section 2 interference can be suppressed.

[Auxiliary fan]
An exhaust auxiliary fan may be provided on the hot aisle HL side of the host machine 11 to assist the exhaust from the host machine 11 so that the exhaust EAH flows through the gap D more smoothly. Further, an auxiliary suction fan may be provided on the cold aisle CL side of the host machine 11 for assisting the suction of the supplied air to the host machine 11 . Of course, both auxiliary fans may be provided.

As a result, it is possible to positively ventilate the inside of the host machine 11 with cold air to secure the necessary air volume, and the inside of the host machine 11 can be cooled without any trouble. In this case, a general-purpose control method can be used for air volume control (rotational speed control). For example, the rotational speed can be controlled so that the pressure on the inlet side of the auxiliary fan becomes zero. It is desirable to start the auxiliary fan earlier than the cooling fans inside the storage cabinets 21 - 26 or the cooling fans inside the host machine 11 . By doing so, it is possible to prevent the auxiliary fan from stopping due to the startup of the cooling fan in the server device.

When employing such an auxiliary fan, for example, like the cooling system 1 shown in FIG. An auxiliary exhaust fan 61 may be provided on the exhaust surface 11b. As a result, the system configuration can be simplified, and the air volume necessary for properly cooling the host machine 11 can be ensured.

Furthermore, as shown in FIG. 7, not only the shielding plate 41 is provided on the hot aisle HL side above the host machine 11, but also the shielding plate 42 is provided on the cold aisle CL side to provide an exhaust auxiliary fan 61 and a suction auxiliary fan 61, respectively. A fan 62 may be provided. Even in such a case, it is possible to secure the air volume necessary for properly cooling the host machine 11 . In this example as well, the rotational speed of the auxiliary exhaust fan 61 is controlled so that the pressure on the inlet side becomes 0, and the rotational speed of the auxiliary suction fan 62 on the cold aisle CL side is controlled so that the same air volume is obtained. You may do so.

The host machine 11 as the first server equipment described above generally uses an axial fan as a cooling fan, and the storage cabinets 21 to 26 as the second server equipment usually use centrifugal fans. are used, the cooling fans employed in the first server device and the second server device in the present invention are not limited to such axial fans and centrifugal fans, respectively. In other words, the cooling fan used in the first server device may have a characteristic of easily obtaining an air volume larger than that of the cooling fan employed in the second server device. The cooling fan used in the first server device may have a characteristic of easily obtaining a higher static pressure than the cooling fan employed in the first server device.

In the above-described embodiment, the heat exchange section 2 is provided above the server rack 3 inside the outer casing 5 , but may be provided on the side of the server rack 3 .

In the above example, the gap D was formed between the upper surface side of the host machine 11 and the lower surface side of the storage cabinet 21, but the gap D should be secured as a passage for the warm air from the host machine 11 to flow. Therefore, it may be formed on the side or bottom surface of the host machine 11 .

INDUSTRIAL APPLICABILITY The present invention is useful for cooling a system in which various electronic devices, such as a server, which generate heat and have a cooling fan as a countermeasure, are mounted on a rack or the like.

1 cooling system 2 heat exchange unit 3 server rack 5 outer casing 11 host machine 11a suction surface 11b exhaust surface 21-26 storage cabinet 21a-26a suction surface 21b-26b exhaust surface 31, 32 sealing material 41, 42 shield plate 51 convection suppression Plate CL Cold aisle D Gap HL Hot aisle

Claims (10)

a rack in which a first server device having a first fan as a cooling fan and a second server device having a second fan having an air volume characteristic smaller than that of the first fan as a cooling fan are provided;
a heat exchange device disposed on the top or side of the rack and used for cooling the first server device and the second server device;
a first space formed on the suction sides of the first server device and the second server device;
A server cooling system comprising: a second space formed on the blow-out side of the first server device and the second server device,
The first fan used in the first server device has a characteristic of easily obtaining an air volume larger than that of the second fan used in the second server device,
The second fan used in the second server device has a characteristic that a static pressure higher than that of the first fan used in the first server device is easily obtained,
Having a flow path for guiding the air blown out from the second server device to the suction side of the first server device, and directing the air blown out from the first server device to the blowout side of the second server device A server cooling system, comprising: a shielding plate that inhibits the flow of water. 2. The server cooling system according to claim 1, wherein the second space has a shielding plate that separates the blow-out side area of the first server device from the blow-out side area of the second server device. . 3. The apparatus according to claim 1, wherein an airtight space is secured in the upper portion, the lower portion, or the side portion of the second server device, through which the air blown out from the second server device passes. 1. The server cooling system according to claim 1. A convection prevention plate having a depth equal to or greater than the height of the void in the first space and having a width equal to or greater than the width of the second server device is provided above the void in the first space. A server cooling system as described. 5. The server cooling system according to claim 4, wherein the position of the suction surface of the first server device is offset from the edge of the convection prevention plate by a distance equal to or greater than the height of the gap. . 6. The server cooling system according to claim 4, wherein the width of said first space is equal to or narrower than each width of said first server device and said second server device. 7. The server cooling system according to any one of claims 1 to 6, further comprising a blowout auxiliary fan on the side of said second space for assisting blowout of air from said second server device. 8. The server cooling system according to any one of claims 1 to 7, further comprising an auxiliary suction fan for assisting suction of the first server device on the side of the first space. 9. The server cooling system according to claim 1, wherein said first fan is a centrifugal fan and said second fan is an axial fan. a rack in which a first server device having a first fan as a cooling fan and a second server device having a second fan having an air volume characteristic smaller than that of the first fan as a cooling fan are provided;
a heat exchange device disposed on the top or side of the rack and used for cooling the first server device and the second server device;
a first space formed on the suction sides of the first server device and the second server device;
a second space formed on the blowout side of the first server device and the second server device;
A server cooling method including a shielding plate that prevents the air blown from the first server device from flowing to the blowing side of the second server device,
The first fan used in the first server device has a characteristic of easily obtaining an air volume larger than that of the second fan used in the second server device,
The second fan used in the second server device has a characteristic that a static pressure higher than that of the first fan used in the first server device is easily obtained,
A server cooling method, wherein the air blown out from the second server device is led to the suction side of the first server device.

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